CN110100118A - Torque coupling arrangement and its manufacturing method with torque-vibration damper and unidirectional turbine clutch - Google Patents

Abstract

A hydrodynamic torque converter includes a housing with locking surfaces, an impeller and turbine, a one-way turbine clutch, and a torsional vibration damper. The one-way turbine clutch includes an outer ring non-rotatably connected to the turbine housing, an inner ring, and an engagement member that allows rotational movement of the outer ring relative to the inner ring in only one circumferential direction. The turbine is non-rotatably coupled to the outer ring of the one-way turbine clutch. The torsional vibration damper includes an input member, a plurality of circumferentially acting elastic members, and an output member elastically coupled to the input member through the elastic members. The output member of the torsional vibration damper is non-rotatably attached to the turbine.

Description

Torque coupling device with torsional vibration damper and one-way turbine clutch and the same Manufacturing method

technical field

The present invention relates generally to fluid coupling devices, and more particularly to a torque converter for a hybrid vehicle having a one-way clutch for a turbine and a method of making the same.

Background technique

Currently, the demand for "cleaner" vehicles tends to increase due to the need to reduce fuel consumption and limit pollution. Generally, in order to achieve the above-mentioned needs, a hybrid system is being developed. Hybrid vehicles, for example, are known to have torque converters and regenerative braking, where an alternator (or generator) is used to harvest kinetic energy during vehicle braking. The alternator converts the collected kinetic energy into electrical energy, for example to charge an energy storage device in the form of a bank of supercapacitors or batteries. This recovered energy is then returned to the various electrical and electronic devices included in the motor vehicle. The electrical energy can also be used to start the heat engine, or to assist the heat engine's torque.

In some operating conditions of a hybrid vehicle, such as in coasting mode, engine braking mode, and regeneration mode, the output hub for the torque converter may spin faster than the turbine of the torque converter. Typically, the output hub and turbine are non-rotatingly connected. Thus, in coasting, engine braking, or regeneration modes, the rotation of the turbine reverses the typical fluid flow pattern in the converter, and the turbine "pumps" fluid to the impeller. Such operation of the turbine is undesirable because the rotation of the turbine heats the oil in the torque converter, resulting in excessive heat loss and, in some cases, even damage to the torque converter.

Furthermore, during coasting of the hybrid vehicle, drag caused by the turbine of the torque converter reduces the efficiency of the electric motor of the hybrid vehicle because the drag creates reverse torque and reduces the effective torque of the electric motor.

Also, under some operating conditions, such as regeneration mode in a hybrid vehicle, it is desirable to prevent rotation of the internal combustion engine. Additionally, the rotation of the turbine can transfer some of the torque to the impeller and then to the internal combustion engine. It is known to use mechanical devices, such as one-way clutches or gear mechanisms, to disconnect the input shaft from the torque associated with the regeneration mode.

SUMMARY OF THE INVENTION

technical problem

While conventional hydrodynamic torque coupling devices, including but not limited to those discussed above, have proven useful in hybrid vehicles, allowing the turbine of a torque converter used with hybrid vehicles to be removed from the transmission input shaft during regeneration mode Improvements to the disconnected one-way clutch are possible, which could enhance its performance and cost.

solution to the problem

According to a first aspect of the present invention, there is provided a hydrodynamic torque converter for coupling a drive shaft and a driven shaft together. The torque converter includes a housing rotatable about the axis of rotation and having a locking surface, an impeller rotatable about the axis of rotation, a turbine rotatable about the axis of rotation and disposed axially opposite the impeller, and a shaft axially positioned between the impeller and the turbine. Stator, one-way turbine clutch that allows rotational movement of the turbine in only one circumferential direction, and torsional vibration dampers. The turbine is coaxially aligned with the impeller and can be rotationally driven hydrodynamically by the impeller. The one-way turbine clutch includes: an outer ring non-rotatably connected to the turbine; an inner ring disposed radially within the outer ring, and a plurality of engagement members positioned radially between the outer ring and the inner ring, the plurality of The engagement member is configured to allow rotational movement of the outer ring relative to the inner ring in only one circumferential direction. The turbine is non-rotatably coupled to the outer ring of the one-way turbine clutch. The turbine includes a turbine casing and at least one retainer plate extending radially inwardly from the turbine casing integrally with the turbine casing. The at least one retaining plate is disposed between the stator and the turbine one-way clutch. The torsional vibration damper includes an input member rotatable about an axis of rotation, a plurality of circumferentially acting elastic members, and an output member elastically coupled to the input member through the elastic members. The output member of the torsional vibration damper is non-rotatably attached to the turbine.

According to a second aspect of the present invention, there is provided a method for assembling a hydrodynamic torque converter for coupling a drive shaft and a driven shaft together. The method includes the steps of: providing a first housing shell and a second housing shell of a housing rotatable about an axis of rotation; providing a pre-assembled torque converter including an impeller, an impeller shaft opposingly disposed turbine and stator; and providing a one-way turbine clutch that allows rotational movement of the turbine in only one circumferential direction. The turbine includes a turbine casing and at least one retainer plate extending radially inwardly from the turbine casing integrally with the turbine casing. The one-way turbine clutch includes: an outer ring; an inner ring disposed radially within the outer ring; and a plurality of engagement members positioned radially between the outer ring and the inner ring, the plurality of engagement members configured to allow the outer ring There is only a rotational movement in one circumferential direction relative to the inner ring. The method also includes the steps of non-rotatably connecting the turbine to the outer ring of the one-way turbine clutch coaxially with the axis of rotation, such that at least one retaining plate of the turbine is disposed between the stator and the turbine one-way clutch, torsional vibration dampers including an input member rotatable about an axis of rotation, a plurality of circumferentially acting elastic members, and an output member elastically coupled to the input member through the elastic members, non-rotatably attaching the output member of the torsional vibration damper to the turbine, and The input member of the torsional vibration damper is elastically mounted to the output member of the torsional vibration damper by a circumferentially acting elastic member.

Other aspects of the invention, including apparatus, devices, systems, converters, processes, etc., which form a part of this invention, will become more apparent upon reading the following detailed description of the exemplary embodiments.

Description of drawings

The accompanying drawings are incorporated in and constitute a part of this specification. The accompanying drawings, together with the general description given above and the detailed description of exemplary embodiments and methods given below, serve to explain the principles of the invention. Objects and advantages of the present invention will become apparent from a study of the following specification in light of the accompanying drawings, in which like elements have been given the same or similar reference numerals, and in the drawings:

1 is a partial half view in axial section of a hydrodynamic torque converter according to a first exemplary embodiment of the present invention;

2 is a partial half view in axial section of the turbine, one-way turbine clutch and lockup piston of the hydrodynamic torque converter according to the first exemplary embodiment of the present invention;

3 is a partial half view in axial section of the turbine and one-way turbine clutch of the hydrodynamic torque converter according to the first exemplary embodiment of the present invention;

4 is a cross-sectional half view of the one-way turbine clutch of FIG. 3;

5 is a front plan view of the outer ring of the one-way turbine clutch of the hydrodynamic torque converter according to the first exemplary embodiment of the present invention;

6 is a perspective view of an outer ring of a one-way turbine clutch of a hydrodynamic torque converter according to the first exemplary embodiment of the present invention;

7A is a partial perspective front view of a turbine of a hydrodynamic torque converter in accordance with the first exemplary embodiment of the present invention;

7B is a perspective view of a replacement turbine of a hydrodynamic torque converter in accordance with the first exemplary embodiment of the present invention;

8 is a perspective view of a turbine having a one-way turbine clutch of a hydrodynamic torque converter according to the first exemplary embodiment of the present invention;

9 is a rear plan view of a turbine of a hydrodynamic torque converter with a one-way turbine clutch mounted thereto in accordance with the first exemplary embodiment of the present invention;

10 is a partial half view in axial section of a hydrodynamic torque converter according to a second exemplary embodiment of the present invention;

11 is a partial half view in axial section of a turbine and one-way turbine clutch of a hydrodynamic torque converter according to a second exemplary embodiment of the present invention;

Figure 12 is a cross-sectional half view of the one-way turbine clutch of Figure 11;

13 is a partial half view in axial section of a hydrodynamic torque converter according to a third exemplary embodiment of the present invention;

14 is a partial half view in axial section of the turbine, one-way turbine clutch and lockup piston of a hydrodynamic torque converter according to a third exemplary embodiment of the present invention;

15 is a partial half view in the axial interface of the turbine and one-way turbine clutch of a hydrodynamic torque converter according to a third exemplary embodiment of the present invention;

Figure 16 is a cross-sectional half view of the one-way turbine clutch of Figure 15;

17A is a partial perspective front view of a turbine of a hydrodynamic torque converter according to a third exemplary embodiment of the present invention;

17B is a partial perspective rear view of a turbine of a hydrodynamic torque converter according to a third exemplary embodiment of the present invention;

18 is a rear plan view of a turbine of a hydrodynamic torque converter with a one-way turbine clutch mounted thereto in accordance with a third exemplary embodiment of the present invention;

19 is a partial half view in axial section of a hydrodynamic torque converter according to a fourth exemplary embodiment of the present invention;

20 is a partial half view in axial section of the turbine, one-way turbine clutch and lockup piston of a hydrodynamic torque converter according to a fourth exemplary embodiment of the present invention;

20 is a partial half view in axial section of a turbine and one-way turbine clutch of a hydrodynamic torque converter according to a fourth exemplary embodiment of the present invention;

21 is a partial half view in axial section of a turbine and one-way turbine clutch of a hydrodynamic torque converter according to a fourth exemplary embodiment of the present invention; and

FIG. 22 is a cross-sectional half view of the one-way turbine clutch of FIG. 21 .

Detailed ways

Reference will now be made in detail to exemplary embodiments and methods of the present invention as illustrated in the accompanying drawings, wherein like reference numerals refer to like or corresponding parts throughout. It should be noted, however, that the invention in its broader aspects is not limited to the specific details, representative apparatus and method, and illustrative examples shown and described in connection with the exemplary embodiments and methods.

This description of exemplary embodiments is intended to be read in conjunction with the accompanying drawings, which are considered to be a part of the entire written description. In the specification, terms such as "horizontal", "vertical", "up", "down", "up", "down", "right", "left", "top" and "bottom" and their derivatives ( For example, "horizontal," "downward," "upward," etc.) should be construed to refer to the orientation described below or as shown in the figures in question. These relative terms are for convenience of description and are generally not intended to require a particular orientation. Terms such as "connected" and "interconnected" with reference to attachments, couplings, etc. refer to relationships in which structures are fastened or attached to each other, either directly or indirectly through intermediate structures, as well as movable or rigid attachments connection or association, unless expressly stated otherwise. The term "operably connected" is an attachment, coupling, or connection that allows the related structure by virtue of the relationship to operate as intended. In addition, the terms "a" and "an" as used in the claims mean "at least one".

A first exemplary embodiment of a fluid dynamic torque converter, such as for use in a hybrid vehicle, is generally indicated in the drawings by the reference numeral 10, as best shown in the partial cross-sectional views of FIGS. 1-4. The hydrodynamic torque converter 10 may operate in a known manner to fluidly couple drive and driven shafts of a motor vehicle (eg, an automobile). Typically, the drive shaft is the output shaft of the motor vehicle's internal combustion engine (not shown), and the driven shaft is connected to the motor vehicle's automatic transmission.

The hydrodynamic torque converter 10 includes a sealed housing 12 rotatable about an axis of rotation X, a fluid coupling 14 all disposed in the housing 12, a torsional vibration damper (also referred to herein as a damper assembly) 16, and A friction lock-up clutch 18 is also rotatable about the axis of rotation X. The sealed housing 12 is at least partially filled with a fluid, such as oil or transmission fluid. A torsional vibration damper 16 and a friction lock-up clutch 18 are also provided in the housing 12 . The figures discussed herein show a half view, ie, a portion or section of the hydrodynamic torque converter 10 above the axis of rotation X. As a whole, the torque converter 10 is symmetrical about the axis of rotation X. Herein, axial and radial orientations are considered relative to the rotational axis X of the torque converter 10 . Relative terms such as "axially", "radially" and "circumferentially" are oriented with respect to being parallel to, perpendicular to and circumferentially about the axis of rotation X, respectively.

The sealed casing 12 according to the first exemplary embodiment shown in FIG. 1 includes a first casing shell (or cover shell) 20 ₁ and a second casing shell (or impeller casing) 20 ₂ , the first casing shell 201 and the _second housing shell 202 are non _- movably (ie fixedly) hermetically interconnected, such as by welding on their outer peripheries at the weld seam 19, but still rotatable about the axis of rotation X . The first housing shell 12c is non-removably (ie, fixedly) interconnected to a drive shaft, more typically a flywheel (not shown), which is fixed to the drive shaft so as to be non-rotatable relative to the drive shaft , so that the housing 12 rotates at the same speed as the engine is operating for transmitting torque. Specifically, in the embodiment shown in FIG. 1 , the housing 12 is rotatably driven by the internal combustion engine and is non-rotatably coupled to its flywheel by means of bolts 21 . Typically, studs 21 are fixedly fastened to this housing 20 ₁ , eg by welding. Each of the _first housing shell 201 and the _second housing shell 202 is one-piece (ie, one-piece) or one-piece, and may be integrally made, for example, by a press-formed one-piece metal sheet. The _first housing shell 201 defines a locking surface 25 that faces the fluid coupling 14 and damper assembly 16 within the housing 12 , as best shown in FIG. 1 .

The fluid coupling 14 includes an impeller (sometimes referred to as a pump) 30 , a turbine 32 and a stator (sometimes referred to as a reactor) 34 interposed axially between the impeller 30 and the turbine 32 . The impeller 30 , the turbine 32 and the stator 34 are coaxially aligned with each other on the axis of rotation X. The impeller 30, turbine 32 and stator 34 together form a torus. As is known in the art, the impeller 30 and the turbine 32 may be fluidly (or hydrodynamically) coupled to each other.

The impeller 30 includes a substantially annular, semi-annular (or concave) impeller casing 31 , a substantially annular impeller core ring 36 , and fixedly (ie, immovably) attached to the impeller casing 31 and the impeller core ring 36 impeller blades 37, for example by brazing. At least a portion of the _second housing shell 202 of the housing 12 forms and serves as the impeller shell 31 of the impeller assembly 30 . Accordingly, the impeller housing 31 is sometimes referred to as a portion of the housing 12 . As a result, the impeller casing 31 of the impeller 30 is non-rotatable relative to the _first housing casing 201, and therefore non-rotatable relative to the drive shaft (or flywheel) of the engine, and rotates at the same speed as the engine output. The impeller 30 also includes an impeller hub 22 fixedly secured to the _second housing shell 202 (or impeller shell 31). The impeller hub 22 is arranged to engage with the hydraulic pump of the transmission. The impeller housing 31 , the impeller core ring 36 and the impeller blades 37 are typically formed by stamping from a billet.

Turbine 32 includes a substantially annular turbine casing 33, a substantially annular turbine core ring 38, and a plurality of turbine blades 39 fixedly (ie, immovably) attached to the turbine casing 33 and core ring 38, for example by brazing. Rotation of the impeller 30 causes the transmission fluid in the annulus to rotate the turbine blades 36 and thus the turbine casing 33 . Turbine casing 33, turbine core ring 30 and turbine blades 31 are typically formed by stamping from billet.

The stator 34 is positioned between the impeller 30 and the turbine 32 to redirect fluid from the turbine 32 back to the impeller 30 in an efficient manner. The stator 34 is typically mounted on a one-way stator clutch 40 to prevent reverse rotation of the stator 34 . The _first thrust bearing 421 is interposed between the stator 34 and the turbine casing 33, and the _second thrust bearing 422 is interposed between the stator 34 and the impeller hub 22 of the casing 12 or the _second casing casing 202.

As best shown in FIG. 1, the one-way stator clutch 40 is mounted within the stator hub 35 of the stator 34 and includes an outer ring 44 coaxial with the axis of rotation X, an inner ring 46 coaxial with the axis of rotation X, and A plurality of wedges or cylindrical rollers 48 are circumferentially disposed in the annular space defined between the outer ring 44 and the inner ring 46 . The inner peripheral surface of the inner ring 46 has splines 47 for rotatably coupling to the outer periphery of the stator shaft.

The stator 34 includes an annular stator retaining plate 50 to retain the one-way stator clutch 40 within the stator hub 35 and prevent axial movement of the components of the one-way stator clutch 40 relative to the stator hub 35 in the direction of the axis of rotation X. The stator retention plate 50 has axially inner end surfaces that engage the outer and inner rings 44 and 46 of the one-way stator clutch 40 to retain the sprags or cylindrical rollers 48 within the stator hub 35 . The axially outer end face of the stator holding plate 50 is engaged with the _first thrust bearing 421. According to the first exemplary embodiment, the stator holding plate 50 is fastened to the stator hub 35 of the stator 34 .

The lock-up clutch 18 includes a substantially annular lock-up piston 52 that can be directed along the axis of rotation X toward the lock-up surface 25 within the cover housing 12c of the housing 12 (the engaged position (or lock-up mode) of the lock-up clutch 18 ) ) axial displacement and away from the locking surface 25 (the disengaged position (or non-locking) of the lock-up clutch 18 ) in the cover housing 12 c of the housing 12 . In other words, the locking piston 52 is selectively pressed against the locking surface 25 of the housing 12 , thereby locking the torque converter 10 between the shafts and thus controlling the sliding movement between the turbine 32 and the impeller 30 .

The locking piston 52 includes a substantially annular piston body 54 and an annular friction lining 56 fixedly attached to the piston body 54 to face the locking surface 25 of the housing 12 . The piston body 54 has an engagement surface 55 axially facing the locking surface 25 of the housing 12 . As best shown in FIG. ₁ , the annular friction lining 56 is fixedly attached to the piston body 54 at the radially outer peripheral end 541 of the piston body 54 by any suitable means known in the art, such as by gluing. Engagement surface 55 . Extending axially at the radially inner peripheral end ₅₄₂ of the piston body 54 is a substantially cylindrical flange 58 adjacent and coaxial with the axis of rotation X.

The annular friction lining 56 is made of friction material to improve friction performance. Alternatively, annular friction linings may be fastened to the locking surface 25 of the housing 12 . According to yet another embodiment, a first friction ring or lining is fastened to the locking surface 25 of the housing 12 and a second friction ring or lining is fastened to the engagement surface 55 of the locking piston body 54 . It is within the scope of the present invention to omit one or both of the friction rings. In other words, the annular friction lining 56 may be fastened to any, all or none of the engagement surfaces. Furthermore, according to the exemplary embodiment, the engagement surface 55 of the lockup piston body 54 is slightly tapered to improve engagement of the lockup clutch 18 . Specifically, the engagement surface 55 of the locking piston body 54 that retains the annular friction lining 55 is tapered at an angle of 10° to 30° with the locking surface 25 of the housing 12 to improve the torque capability of the locking clutch 18 . Alternatively, the engagement surface 55 of the locking piston body 54 may be parallel to the locking surface 25 of the housing 12 .

The hydrodynamic torque converter 10 also includes a one-way turbine clutch 60 to prevent reverse rotation of the turbine 32 . In other words, the one-way turbine clutch 60 allows rotational movement of the turbine 32 in only one circumferential direction. The one-way turbine clutch 60, as best shown in FIG. 4, includes: an outer ring 62 coaxial with the axis of rotation X; an inner ring 64, coaxial with and radially spaced from the outer ring 62 to allow The outer ring 62 and the inner ring 64 respectively rotate relative to each other; and have a plurality of engagement members 66 circumferentially disposed in the annular space defined between the outer ring 62 and the inner ring 64 . The outer ring 62 has an annular radially outer raceway surface _62R and the inner race 64 has an annular radially inner raceway surface _64R diametrically opposite and spaced from the radially outer raceway surface _62R . As best shown in FIG. 4 , the radially inner raceway surface _64R of the inner ring 64 is disposed radially inboard of the radially outer raceway surface _62R of the outer raceway 62 . Engagement member 66 is configured to engage diametrically opposed outer rail surface 62 _R and inner rail surface 64 _R .

The engagement member 66 is configured to selectively non-rotatably engage the outer ring 62 to the inner ring 64 and selectively rotationally disengage the outer ring 62 from the inner ring 64 . According to an exemplary embodiment of the present invention, the engagement members 66 are wedge elements distributed in the circumferential direction. The wedge type one-way turbine clutch 60 further includes an outer retainer 67o for holding the wedge 66 on the outer peripheral side of the annular space, an inner retainer 67i for retaining the wedge 66 on the inner peripheral side of the annular space, and ribbon springs, as best shown in Figures 2 and 6. The band spring is an annular spring member configured to bias the wedge 66 radially between the outer ring 62 and the inner ring 64 by its spring force. The radially outer ends of the wedges 66 are configured to engage the radially outer track surface 62 _R of the outer ring 62 , while the radially inner ends of the wedges 66 are configured to engage the radially inner track surface of the inner ring 64 of the one-way turbine clutch 60 _64R . Alternatively, the engagement members may be rollers or wedge-shaped elements.

In other words, the outer ring 62 may rotate relative to the inner ring 64 of the one-way turbine clutch 60 in only one circumferential direction. The inner peripheral surface of the inner ring 64 has splines 65 for rotatably coupling to the outer periphery of the transmission input shaft. Accordingly, the inner ring 64 of the one-way turbine clutch 60 defines the output hub of the hydrodynamic torque converter 10 . As further shown in FIG. 1 , the cylindrical flange 58 of the piston body 54 is axially slidably (ie, movably) mounted to the output hub 64 . Accordingly, the locking piston 52 is rotationally and axially movable relative to the output hub 64 along the axis of rotation X to enter and exit the locking mode accordingly. A seal member 78 mounted to the radially inner peripheral surface of the output hub 64 forms a seal at the interface of the transmission input shaft and the output hub 64 . Additionally, the turbine 32 is rotatable about the axis of rotation X relative to the output hub 64 .

The output hub 64 has an annular piston flange 68 extending axially outwardly from the output hub 64 and defining a substantially cylindrical piston surface 69 for centering and slidingly engaging the locking piston 52 The cylindrical flange 58 is best shown in FIGS. 1 and 3 . Specifically, the cylindrical flange 58 of the locking piston 52 is mounted to the output hub 64 for centering, rotatable and axially slidable displacement relative to the cylindrical piston surface 69 of the output hub 64 . The output hub 64 also has annular guide ribs 70 that extend axially outward from the output hub 64 and define an annular (eg, cylindrical) radially outer guide surface 71 for centering and centering of the outer ring 62 of the one-way turbine clutch 60 . Radial support, as best shown in Figures 3 and 4. The radially outer piston surface 69 of the piston flange 68 of the output hub 64 includes an annular groove 92 for receiving a sealing member, such as an O-ring 93 .

The outer ring 62 of the one-way turbine clutch 60 includes a body 72 having a substantially cylindrical radially outer surface 73 and including a substantially annular and planar (ie, flat) extending radially inward from the body 72 Guide plate 74 . As best seen in FIG. 3 , the radially inner end (or distal end) 75 of the guide plate 74 slidingly engages the radially outer guide surface 71 of the guide rib 70 of the output hub 64 to allow the outer portion of the one-way turbine clutch 60 to The ring 62 centers and radially supports the outer ring 62 . Additionally, the guide plate 74 is configured to retain the engagement member 66 between the outer ring 62 and the inner ring 64 and prevent the engagement member 66 and the inner ring 64 of the one-way turbine clutch 60 from moving relative to the outer ring 62 along the axis of rotation X Axial movement is performed in a left-to-right direction, as shown in Figure 2. According to an exemplary embodiment of the present invention, the guide plate 74 and the outer ring 62 of the one-way turbine clutch 60 are one-piece (or one-piece) parts, eg, made from a single part, as best shown in FIG. 3 , but also It can be separate parts that are fixedly connected together.

The turbine 32 also includes: one or more (preferably three) coupling members 77A extending substantially axially outward from the radially inner end 33i of the annular turbine casing 33 in _a direction toward the cover casing 201; and _one or more _A number (preferably three) of retaining plates 77R extending generally radially inwardly from the radially inner end 33i of the annular turbine housing 33 past the engagement member 66 and partially overlapping the inner ring 64 of the one-way turbine clutch 60, as shown in FIG. Best shown in 2, 5, 6 and 7A. Each retention plate _77R has an innermost free distal end, as best seen in Figure 7A. According to the first exemplary embodiment of the invention, the turbine casing 33 with the coupling member _77A and the retaining plate _77R is a one-piece (or one-piece) part, eg made from a single part, eg by stamping, but may be Separate parts that are fixedly connected together.

Alternatively, as best shown in Figure 7B, the turbine 32 is replaced by a turbine 32' comprising: a substantially annular turbine casing 33'; one or more (preferably three) coupling members _77A , from the annular A radially inner end 33i of the turbine casing 33' extending substantially axially outward in _a direction towards the cover casing 201; and one or more (preferably three) retaining plates _77R extending from the radially inner end of the annular turbine casing 33' 33i extends generally radially inwardly past engagement member 66 and partially overlaps inner ring 64 of one-way turbine clutch 60 . The innermost ends of the retaining plates _77R are monolithically interconnected by annular portions 77C, as best shown in Figure 7B. The annular portion 77C of the turbine 32 _' provides a bearing contact surface for the first thrust bearing 421. In other words, the _first thrust bearing 421 is sandwiched between the annular portion 77C of the turbine wheel 32 ′ and the stator holding plate 50 . According to the first exemplary embodiment of the present invention, an alternative embodiment of the turbine casing 33' having the coupling member 77A, the retaining plate _77R and the annular portion 77C is _a one-piece (or one-piece) part, eg, made from a single part , for example by stamping, but also separate parts that are fixedly connected together.

As best shown in FIGS. 3-6 , the outer ring 62 of the one-way turbine clutch 60 includes at least one, preferably a plurality of recesses (or recesses) 63 , each recess being associated with a notch in the coupling member _77A of the turbine 32 a complement. Specifically, notches 63 are formed in the cylindrical radially outer surface 73 of the body 72 of the outer ring 62 of the one-way turbine clutch 60 , as best shown in FIGS. 4-7 . Turbine 32 is non-rotatably coupled to outer ring 62 of one-way turbine clutch 60 . Specifically, as best shown in FIGS. 2 , 3 and 8 , each coupling member 77 _A positively engages one of the notches 63 to non-rotatably couple the outer ring 62 of the one-way turbine clutch 60 and turbo 32. According to the first exemplary embodiment of the present invention, the outer ring 62 has three notches 63 and the turbine 32 has three complementary coupling members _77A .

Additionally, the retaining plate _77R of the turbine 32 is disposed between the first thrust bearing 421 and the _one -way turbine clutch 60, as best shown in FIG. 1 . Retaining plate _77R is configured to retain engagement member 66 between outer ring 62 and inner ring 64 and prevent engagement member 66 and inner ring 64 of one-way turbine clutch 60 from moving from the right relative to outer ring 62 along axis of rotation X. Axial movement in the direction to the left, as shown in Figure 1-3.

In some operating conditions of the hybrid vehicle, such as in coasting mode, engine braking mode, and regeneration mode, the output hub 64 for the torque converter 10 may spin faster than the turbine 32 of the torque converter 10 . Thus, the one-way turbo clutch 60 prevents drag created by the turbine 32 and prevents reverse torque (which typically reduces the efficiency of the hybrid vehicle's electric motor) to avoid reducing the effective torque of the hybrid vehicle's electric motor. In other words, the one-way turbo clutch 60 decouples the turbine 32 from the output hub 64 of the torque converter 10 under some operating conditions of the hybrid vehicle, such as in coasting mode, engine braking mode, and regeneration mode.

The torsional vibration damper 16 is accommodated axially in the casing 12 between the turbine 32 and the first casing shell 201 of the casing 12, as shown in FIG. ₁ . The torsional vibration damper 16 includes a substantially annular drive (or input) member 80, a plurality of circumferential elastic damping members 82 equidistantly spaced from each other in the circumferential direction, and at least one, preferably a plurality of drive (or output) member 84. According to the first exemplary embodiment of FIG. 1 , the elastic damping member 82 is configured as a helical (or coil) spring, the major axis of which is oriented substantially in the circumferential direction. Other resilient members may be selected in place of or in addition to spring 82 . Drive member 80 and driven member 84 engage circumferentially opposite ends of resilient damping member 82 . Accordingly, the drive member 80 is resiliently coupled to the driven member 84 through a resilient damping member 82, as is known in the art. Accordingly, the driven member 84 of the damper assembly 16 may rotate relative to the drive member 80 due to the resiliency of the elastic damping member 82 that absorbs torsional vibrations.

According to the first exemplary embodiment, the drive member 80 of the damper assembly 16 and the locking piston body 54 of the locking piston 52 are fixedly (ie, immovably) connected together by rivets 81 , as best seen in FIGS. 1 and 2 . shown. In turn, each driven member 84 is immovably connected (ie, fixedly connected) to the annular turbine casing 33 of the turbine 32 at the radially distal end of the turbine casing 33 of the turbine 32 by suitable means, such as by welding Welded or mechanical fasteners at seam 85. In other words, the locking piston 52 is resiliently coupled to the worm wheel 32 by the resilient damping member 82 for limited relative rotational movement between the locking piston 52 and the worm wheel 32 . Furthermore, since the locking piston 52 is axially movable relative to the output hub 64 along the axis of rotation X, the locking piston 52 is axially movable relative to the output member 84 of the torsional vibration damper 16 .

A lock-up clutch 18 is provided for locking the drive shaft and the driven shaft. The lock-up clutch 18 is typically activated after the motor vehicle is started and after the drive and driven shafts are hydraulically coupled to avoid efficiency losses, particularly those caused by slip phenomena between the turbine 30 and the impeller 32 . The locking piston 52 may be axially toward the locking surface 25 within the housing 12 (the engaged (or locked) position of the lockup clutch 18 ) and away from the locking surface 25 within the housing 12 (the disengaged (or open) position of the lockup clutch 18 ) shift. Additionally, the lockup piston 52 is axially displaceable away from the torsional oscillation damper 16 (the engaged (or locked) position of the lockup clutch 18 ) and toward the torsional oscillation damper 16 (the disengaged (or open) position of the lockup clutch 18 ). Specifically, the cylindrical flange 58 of the locking piston body 54 is mounted to the cylindrical piston surface 69 of the annular piston flange 68 of the output hub 64 for centering, relative to the output hub 64 and the cover housing 201 of the housing ₁₂ Rotationally and axially slidable displacement. As discussed in further detail below, the locking piston 52 is axially movable relative to the cover housing 20 along the axis of rotation X. Axial movement of the lock piston 52 along the output hub 64 is controlled by annular damper pressure chambers 23 ₁ , 23 ₂ positioned on axially opposite sides of the lock piston 54 , as shown in FIG. 1 .

The locking piston 54 is selectively pressed against the locking surface 25 of the housing 12 to lock the torque converter 10 between the drive shaft and the driven shaft, and thereby control the sliding movement between the turbine wheel 32 and the impeller 30 . Specifically, when the appropriate hydraulic pressure is applied to the lock piston 52, the lock piston 52 moves rightward toward the lock surface 25 of the housing 12 and away from the turbine 32 (as shown in FIG. 1) and clamps the friction lining 56 to the piston body between the bonding surface 55 of the housing 54 and the locking surface 25 of the housing 12 . As a result, the lock-up clutch 18 operably connects the housing 12 to the output hub 64 via the torsional vibration damper 16 , the turbine 32 and the one-way turbine clutch 60 when the lock-up clutch 18 is in the locked position. Therefore, when the lock-up clutch 18 is in its locked position, it does not bypass the turbine 32 .

In operation, when the lock-up clutch 18 is in the disengaged (open) position and when the turbine 32 is spinning faster than the output hub 64 , engine torque is transferred from the impeller 30 through the one-way turbine clutch 60 to the turbine 32 of the fluid coupling 14 . Output hub 64 . When the lock-up clutch 18 is in the engaged (locked) position, engine torque is transferred from the housing 12 to the output hub 64 through the torsional vibration damper 16 , the turbine 32 and the one-way turbine clutch 60 . However, the one-way turbo clutch 60 diverts the turbine 32 from the output of the torque converter 10 when the hybrid vehicle is in a coasting mode, an engine braking mode, or a regeneration mode, ie, when the output hub 64 can rotate faster than the turbine 32 . The hub 64 is disengaged and does not transmit torque from the output hub 64 to the turbine 32 .

A method for assembling the fluid dynamic torque converter 10 is as follows. It should be understood that the exemplary method may be practiced in conjunction with other embodiments described herein. This exemplary method is not an exclusive method for assembling the turbine assemblies described herein. While the method for assembling the fluid dynamic torque converter 10 may be implemented by sequentially performing the steps described below, it should be understood that the method may include performing the steps in a different order.

First, the impeller 30 , turbine 32 , stator 34 and torsional vibration damper 16 with locking piston 52 may be pre-assembled. The impeller 30 and turbine 32 are formed by billet stamping or by injection molding of polymeric material. The stator 34 is fabricated by casting or injection molding a polymeric material from aluminum. The impeller 30 , turbine 32 and stator 34 subassemblies are assembled together to form the fluid coupling 14 .

According to a first exemplary embodiment of the present invention, the turbine 32 is formed by: an annular turbine casing 33 ; one or more (preferably three) coupling members 77 _A extending from the radially inner end 33i of the annular turbine casing 33 toward _The direction of the cover casing 201 extends substantially axially outward; and one or more (preferably three) retaining plates 77R extending generally radially inwardly from the radially inner end _33i of the annular turbine casing 33, as shown in FIG. 2 and best shown in 5-7. According to the first exemplary embodiment of the present invention, the turbine casing 33 with the coupling member 77 _A and the retaining plate 77 _R is a one-piece (or monolithic) part, eg made from a single part, but may also be fixedly connected together separate parts.

Then add the one-way turbo clutch 60 . The turbine 32 is mounted to the one-way turbine clutch 60 such that each coupling member 77 _A of the turbine 32 matingly engages a notch formed in the cylindrical radially outer surface 73 of the body 72 of the outer ring 62 of the one-way turbine clutch 60 63 to non-rotatably couple the turbine 32 and the outer ring 62 of the one-way turbine clutch 60 as best shown in FIGS. 1-3 and 8 . The retaining plate 77 _R is provided in the vicinity of the radial left side of the one-way turbine clutch 60 , and is axially opposite to the guide plate 74 of the outer ring 62 of the one-way turbine clutch 60 .

Torsional vibration dampers 16 are then added. The driven member 84 is immovably connected (ie, fixedly connected) to the annular turbine casing 33 of the turbine 32 at the radially distal end of the turbine casing 33 of the turbine 32 by suitable means prior to assembly of the torsional vibration damper 16 , such as by welding or mechanical fasteners at weld 85 . Next, the locking piston body 54 of the locking piston 52 is secured to the input member 80 of the torsional vibration damper 16 by suitable means, such as by welding, gluing or fasteners (eg, rivets 81).

The torsional vibration damper 16 is then assembled by elastically coupling the input member 80 to the output member 84 by the elastic damping member 82 . At the same time, the cylindrical flange 58 of the piston body 54 is axially slidably mounted to the output hub 64 . The first housing shell 20 ₁ is then immovably and sealingly fixed to the second housing shell 20 ₂ , for example by welding at 19 , as best shown in FIG. 1 .

Various modifications, changes, and substitutions may be implemented with the above-described embodiments, including, but not limited to, the additional embodiments shown in Figures 10-22. For the sake of brevity, reference features in FIGS. 10-22 discussed above in connection with FIGS. 1-9 will not be described in further detail below, except as necessary or useful to explain additional embodiments of FIGS. 10-22 . Modified parts or sections are indicated by adding the numeral one hundred to the reference numerals of the parts or sections.

In the hydrodynamic torque converter 110 of the second exemplary embodiment shown in FIGS. 10-12 , the one-way turbine clutch 60 is replaced by a one-way turbine clutch 160 . The hydrodynamic torque converter 110 of FIGS. 10-12 substantially corresponds to the hydrodynamic torque converter 10 of FIGS. 1-9 , so only the one-way turbine clutch 160 that is primarily different will be described in detail below.

According to a second exemplary embodiment of the present invention as best shown in FIGS. 10-12 , one-way turbine clutch 160 is configured to prevent reverse rotation of turbine 32 . In other words, similar to the one-way turbine clutch 60, the one-way turbine clutch 160 allows rotational movement of the turbine 132 in only one circumferential direction. One-way turbine clutch 160, best shown in FIG. 11, includes: outer ring 62 coaxial with axis of rotation X; inner ring 164 coaxial with outer ring 62 and radially spaced from outer ring 62 to allow for The outer ring 62 and the inner ring 164 respectively rotate relative to each other; and have a plurality of engagement members 66 circumferentially disposed in the annular space defined between the outer ring 62 and the inner ring 164 .

Also similar to the one-way turbine clutch 60, the outer ring 62 of the one-way turbine clutch 160 has an annular radially outer race surface _62R , and the inner race 164 has an annular diameter diametrically opposite and spaced from the radially outer raceway surface _62R Inward track surface _164R . As best seen in FIG. 12 , the radially inner raceway surface _164R of the inner ring 164 is disposed radially inboard of the radially outer raceway surface _62R of the outer raceway 62 . Engagement member 66 is configured to engage diametrically opposed outer track surface 62 _R and inner track surface 164 _R .

The one-way turbine clutch 160 also accordingly includes low friction annular sliding first and second bearing washers 94 and 95 . A low friction first bearing washer 94 is disposed axially between the retaining plate _77R of the turbine 32 and the inner ring 164 of the one-way turbine clutch 160 so that when the outer ring 62 of the turbine clutch 160 rotates relative to its inner ring 164 Reduce friction between them. The first bearing washer 94 fits into a corresponding annular recess in the left axial outer side wall of the inner ring 164 of the one-way turbine clutch 160, as best shown in Figures 10-12. Similarly, a second bearing washer 95 is axially disposed between the guide plate 74 of the outer ring 62 of the one-way turbine clutch 160 and the annulus of the inner ring 164 of the one-way turbine clutch 160 to reduce friction in the one-way turbine clutch 160 The friction between the outer ring 62 as it rotates relative to its inner ring 164. A low friction second bearing washer 95 fits into a corresponding annular recess in the right axial outer side wall of the inner ring 164 of the one-way turbine clutch 160, as best shown in Figures 10-12.

Each of the low friction first and second bearing washers 94 and 95 is made of a durable low friction material such as phenolic (or phenolic resin) or nylon. Other suitable durable and low friction plastics or other materials may also be used. The first and second bearing washers 94 and 95 reduce friction and wear of the components of the one-way turbine clutch 160 .

Additionally, retaining plate _77R of turbine 32 is configured to retain engagement member 66 between outer ring 62 and inner ring 164 and prevent first bearing washer 94 , inner ring 164 and engagement member 66 of one-way turbine clutch 160 from relative to Axial movement of the outer ring 62 in the direction from right to left along the axis of rotation X, as shown in FIG. 11 . Similarly, guide plate 74 is configured to retain engagement member 66 between outer ring 62 and inner ring 164 and prevent second bearing washer 95 , inner ring 164 , and engagement member 66 of one-way turbine clutch 160 from relative to outer ring 62 Axial movement in the direction from left to right along the axis of rotation X, as shown in FIG. 11 .

In the hydrodynamic torque converter 210 of the third exemplary embodiment shown in FIGS. 13-17 , turbine 32 is replaced by one-way turbine 232 and one-way turbine clutch 60 is replaced by one-way turbine clutch 260 . The hydrodynamic torque converter 210 of FIGS. 13-17 substantially corresponds to the hydrodynamic torque converter 10 of FIGS. 1-9 , so only the turbine 232 and the one-way turbine clutch 260, which are primarily different, will be described in detail below. One-way turbine clutch 260 is configured to prevent reverse rotation of turbine 232 . In other words, the one-way turbine clutch 260 allows rotational movement of the turbine 232 in only one circumferential direction.

According to a third exemplary embodiment of the present invention, turbine 232 is formed with annular turbine casing 233 and a generally annular retaining plate 277R extending generally radially inwardly from radially inner end _233i of annular turbine casing 233, as shown in FIG. 14 . and 15 are best shown. According to the third exemplary embodiment of the present invention, the turbine casing 233 with the retaining plate _277R is an integral (or monolithic) part, eg made from a single part, but may be separate parts that are fixedly connected together.

One-way turbine clutch 260, best shown in FIG. 15, includes: outer ring 262 coaxial with axis of rotation X; inner ring 64 coaxial with outer ring 262 and radially spaced from outer ring 262 to allow for The outer ring 262 and the inner ring 64 respectively rotate relative to each other; and a plurality of engagement members 66 disposed circumferentially in the annular space defined between the outer ring 262 and the inner ring 64 . Outer ring 262 has an annular radially outer raceway surface _262R and inner race 64 has an annular radially inner raceway surface _64R diametrically opposite and spaced apart from radially outer raceway surface _262R . As best shown in FIG. 15 , the radially inner raceway surface _64R of the inner ring 64 is disposed radially inboard of the radially outer raceway surface _262R of the outer ring 262 . Engagement member 66 is configured to engage diametrically opposed outer rail surface 262 _R and inner rail surface 64 _R .

Turbine 232 is non-rotatably attached (ie, fixed) to outer ring 262 of one-way turbine clutch 260 . Specifically, as best shown in FIGS. 15 , 17A, 17B and 18 , the retaining plate 277 _R of the turbine 232 is immovably attached (ie, fixed) to the outer ring 262 of the one-way turbine clutch 260 by suitable means 16 , such as by welding, bonding, or fasteners, such as threaded fasteners 261 that threadedly engage threaded holes 276 in the body 272 of the outer ring 262 of the one-way turbine clutch 260 , as best shown in FIG. 16 . An annular retaining plate 277 _R is fixedly attached to the body 272 of the inner ring 262 of the one-way turbine clutch 260 axially opposite the guide plate 274 of the outer ring 262 of the one-way turbine clutch 260 .

Additionally, the retaining plate 277R of the turbine 232 is disposed between the first thrust bearing 421 and the one-way turbine clutch 260 , as best shown in FIG. 13 . Retaining plate 277R is configured to retain engagement member 66 between outer ring 262 and inner ring 64 and prevent engagement member 66 and inner ring 64 of one-way turbine clutch 260 from moving from right to Axial movement in the left direction, as shown in Figure 13.

In operation, when the lock-up clutch 18 is in the disengaged position (non-lock-up mode), engine torque is transferred from the impeller 30 by the fluid coupling 214 to the driven shaft through the one-way turbine clutch 260 . When the lock-up clutch 18 is in the engaged (locked) position (ie, when the lock-up piston 52 is engaged (or locked) against the locking surface 25 of the housing 12 by the action of hydraulic pressure), engine torque is driven by the housing 12 It is transmitted to the driven shaft via the torsional vibration damper 16 . Specifically, engine torque is transferred from the housing 12 to the lock piston 52 , then from the lock piston 52 to the input member 80 of the torsional vibration damper 16 , and then from the input member 80 through the elastic damping member 82 to the input member 80 of the torsional vibration damper 16 . The driven member 84 is then transmitted from the turbine wheel 232 (fixed to the driven member 84 ) to the driven shaft through the one-way turbine clutch 260 .

A method for assembling the hydrodynamic torque coupling device 210 is as follows. First, the impeller 30 , turbine 232 , stator 34 and torsional vibration damper 16 with locking piston 52 may be pre-assembled. Impeller 30 and turbine 232 are formed by billet stamping or by injection molding of polymeric material. The stator 34 is fabricated by casting or injection molding polymeric material from aluminum. The impeller 30 , turbine 232 and stator 34 subassemblies are assembled together to form the fluid coupling 214 .

According to a third exemplary embodiment of the present invention, the turbine 232 is formed with an annular turbine casing 233, and an annular retaining plate 277R extending generally radially inwardly from the radially inner end 233i of the annular turbine casing 233, as best seen in FIG. 15 . shown. According to the third exemplary embodiment of the present invention, the turbine casing 233 with the retaining plate 277R is an integral (or monolithic) part, eg made from a single part, but may also be separate parts fixedly connected together.

The one-way turbo clutch 260 is then added. The turbine 232 is immovably attached to the one-way turbine clutch 260 such that the retaining plate _277R of the turbine 232 is immovably attached to the body 272 of the outer ring 262 of the one-way turbine clutch 260 by a suitable means, such as by welding, gluing, etc. Connections or fasteners, such as threaded fasteners 261. More specifically, annular retaining plate 277 _R is fixedly attached to outer ring 262 of one-way turbine clutch 260 axially opposite guide plate 274 of outer ring 262 of one-way turbine clutch 260 .

The driven member 84 is then immovably connected (ie, fixed) to the annular turbine casing 233 of the turbine 232 at the radially distal end of the turbine casing 233 of the turbine 232 by suitable means, such as by welding at weld 85 or Mechanical Fasteners. Next, the locking piston body 54 of the locking piston 52 is secured to the input member 80 of the torsional vibration damper 16 by suitable means, such as by welding, gluing or fasteners such as rivets 81 .

The torsional vibration damper 16 is then assembled by elastically coupling the input member 80 to the output member 84 by the elastic damping member 82 . At the same time, the cylindrical flange 58 of the piston body 54 is axially slidably mounted to the cylindrical piston surface 69 of the output hub 64 . The first housing shell 20 ₁ is then immovably and sealingly fixed to the second housing shell 20 ₂ , for example by welding at 19 , as best shown in FIG. 1 .

In the hydrodynamic torque converter 310 of the fourth exemplary embodiment shown in FIGS. 19-22 , the one-way turbine clutch 260 is replaced by a one-way turbine clutch 360 . The hydrodynamic torque converter 110 of FIGS. 19-22 substantially corresponds to the hydrodynamic torque converter 210 of FIGS. 13-18 , so only the slightly different one-way turbine clutch 360 will be described in detail below.

According to a fourth exemplary embodiment of the present invention as best shown in FIGS. 19-22 , one-way turbine clutch 360 is configured to prevent reverse rotation of turbine 232 . In other words, similar to one-way turbine clutch 260, one-way turbine clutch 360 allows rotational movement of turbine 232 in only one circumferential direction. One-way turbine clutch 360, best shown in FIG. 22, includes: outer ring 262 coaxial with axis of rotation X; inner ring 364 coaxial with outer ring 262 and radially spaced from outer ring 262 to allow for The outer ring 262 and the inner ring 364 respectively rotate relative to each other; and have a plurality of engagement members 66 circumferentially disposed in the annular space defined between the outer ring 62 and the inner ring 364 .

Also similar to one-way turbine clutch 260, outer ring 262 of one-way turbine clutch 360 has an annular radially outer track surface _262R , and inner ring 364 has an annular diameter diametrically opposite and spaced from radially outer track surface _262R Inward track surface _364R . As best shown in FIG. 22 , the radially inner raceway surface _364R of the inner ring 364 is disposed radially inboard of the radially outer raceway surface _262R of the outer raceway 262 . Engagement member 66 is configured to engage diametrically opposed outer track surface 262 _R and inner track surface 364 _R .

The one-way turbine clutch 360 also includes low friction annular sliding first and second bearing washers 94 and 95 accordingly. A low friction first bearing washer 94 is disposed axially between the retaining plate _277R of the turbine 232 and the inner ring 364 of the one-way turbine clutch 360 so that when the outer ring 262 of the turbine clutch 360 rotates relative to its inner ring 364 Reduce friction between them. The first bearing washer 94 fits into a corresponding annular recess in the left axially outer sidewall of the inner ring 364 of the one-way turbine clutch 360, as best shown in Figures 10-12. Similarly, a second bearing washer 95 is disposed axially between the guide plate 274 of the outer ring 262 of the one-way turbine clutch 360 and the annulus of the inner ring 364 of the one-way turbine clutch 360 to reduce friction in the one-way turbine clutch 360 The friction between the outer ring 262 as it rotates relative to its inner ring 364. A low friction second bearing washer 95 fits into a corresponding annular recess in the right axial outer side wall of the inner ring 364 of the one-way turbine clutch 360 , as best shown in FIG. 22 .

Each of the low friction first and second bearing washers 94 and 95 is made of a durable low friction material such as phenolic (or phenolic resin) or nylon. Other suitable durable and low friction plastics or other materials may also be used. The first and second bearing washers 94 and 95 reduce friction and wear of the components of the one-way turbine clutch 360 .

Additionally, retaining plate 277 _R of turbine 232 is configured to retain engagement member 66 between outer ring 262 and inner ring 364 and prevent first bearing washer 94 , inner ring 364 and engagement member 66 of one-way turbine clutch 360 from relative to Axial movement of the outer ring 262 in the direction from right to left along the axis of rotation X, as shown in FIG. 21 . Similarly, guide plate 274 is configured to retain engagement member 66 between outer ring 262 and inner ring 364 and prevent second bearing washer 95 , inner ring 364 and engagement member 66 of one-way turbine clutch 360 from relative to outer ring 262 Axial movement in the direction from left to right along the axis of rotation X, as shown in FIG. 21 .

The foregoing description of the exemplary embodiments of this invention has been presented for purposes of illustration in accordance with the provisions of the patent statutes. It is not intended to be exhaustive or to limit the invention to the precise form disclosed. The above-disclosed embodiment was chosen in order to best explain the principles of the invention and its practical application, to thereby enable others of ordinary skill in the art to optimize the various embodiments and various modifications as are suited to the particular use contemplated. The present invention is best utilized so long as the principles described herein are followed. Accordingly, this application is intended to cover any variations, uses, or adaptations of the invention using its general principles. Furthermore, this application is intended to cover such departures from this disclosure as come within known or customary practice in the art to which this invention pertains. Accordingly, changes may be made to the above-described invention without departing from the intent and scope of the invention. The scope of the invention is also intended to be defined by the appended claims.

Claims (20)

1. a kind of dynaflow torque converter, for drive shaft and driven shaft to be linked together, comprising: rotation axis can be surrounded The shell of rotation；It can be around the impeller that rotation axis rotates；It can be rotated around rotation axis and axial relatively with the impeller The turbine of setting, the turbine and the impeller co-axially align can be simultaneously rotatably driven by the impeller hydraulic power；Axis To the stator between the impeller and the turbine；The turbine is allowed only to be rotated in a circumferential direction Unidirectional turbine clutch；And torque-vibration damper；The unidirectional turbine clutch includes: to be non-rotatably connected to institute State the outer ring of turbine；The inner ring being radially arranged in the outer ring；And be positioned radially within the outer ring and the inner ring it Between multiple joint elements, the multiple joint element is configured as allowing the outer ring relative to the inner ring only in a week It is rotated on direction；The turbine is nonrotatably coupling to the outer ring of the unidirectional turbine clutch；Institute State turbine include turbine case and extended radially inwardly from the turbine case and with turbine case one at least one Holding plate, at least one described holding plate are located between the stator and turbine one-way clutch；The twisting vibration damping Device includes can be around the input link of rotation axis rotation, multiple elastic components circumferentially acted on, and pass through elastic component It is elastically attached to the output link of the input link；The output link of the torque-vibration damper is non-rotatably attached To the turbine.

2. dynaflow torque converter according to claim 1, wherein the outer ring of the unidirectional turbine clutch includes having The main body of radially-outer surface and the directing plate extended radially inwardly from the main body.

3. dynaflow torque converter according to claim 2, wherein the radial inner end engagement of the directing plate is described unidirectional The outside guiding surface of the diameter of the inner ring of turbine clutch.

4. dynaflow torque converter according to claim 2 or 3 further includes being axially disposed within the unidirectional turbine clutch The directing plate of outer ring and the inner ring of the unidirectional turbine clutch between low friction bearing washer, with reduce in the list Friction when being rotated to the outer ring of turbine clutch relative to its inner ring between them.

5. the dynaflow torque converter according to any one of claim 2 to 5 further includes being axially disposed within the turbine The bearing washer of low friction between at least one described holding plate and the inner ring of the unidirectional turbine clutch, to reduce in institute State friction between them when turbine is rotated relative to the inner ring of the unidirectional turbine clutch.

6. the dynaflow torque converter according to any one of claim 2 to 5, wherein the turbine further includes at least one A coupling member, at least one described coupling member is from the turbine case along big towards the direction of the unidirectional turbine clutch Cause extends axially outward, and integrated with the turbine case and at least one described holding plate；And wherein, the turbine At least one described coupling member is nonrotatably coupling to the outer ring of the unidirectional turbine clutch.

7. dynaflow torque converter according to claim 6, wherein at least one described coupling member of the turbine is not It is movably attached to the radially-outer surface of the main body of the outer ring of the unidirectional turbine clutch.

8. dynaflow torque converter according to claim 6, wherein the main body packet of the outer ring of the unidirectional turbine clutch Include at least one recess complementary at least one coupling member described in the turbine；And wherein, at least one described connection Connection member matchingly engages at least one described recess, so as not to be rotationally coupled the turbine and the unidirectional turbine clutch The outer ring of device.

9. the dynaflow torque converter according to any one of claim 2 to 5, wherein described at least the one of the turbine A holding plate is nonrotatably coupling to the main body of the outer ring of the unidirectional turbine clutch.

10. dynaflow torque converter according to claim 1, wherein the turbine includes and the turbine case is integrated General toroidal holding plate, and wherein, annular retaining plate is immovably attached to the outer of the unidirectional turbine clutch Ring.

11. dynaflow torque converter according to claim 10 further includes being axially disposed within the unidirectional turbine clutch Inner ring and holding plate between low friction bearing washer, with reduce in the turbine relative to the unidirectional turbine clutch Inner ring rotation when friction between them.

12. dynaflow torque converter according to any one of the preceding claims further includes lock piston, the locking is lived Plug can move axially to the shell and move axially from the shell, selectively to make the locking in lockdown mode Piston is frictionally engaged against the shell.

13. dynaflow torque converter according to claim 12, wherein the lock piston is non-rotatably attached to institute It states input link and the output link relative to the torque-vibration damper can move axially

14. dynaflow torque converter according to claim 12 or 13, wherein the shell has locking surface, wherein The lock piston has the engagement surface for the locking surface for being axially facing the shell, and wherein, the lock piston is also Annular friction liner including being fixedly attached to the engagement surface of the lock piston.

15. dynaflow torque converter according to any one of the preceding claims further includes unidirectional clutch of stator, described Unidirectional clutch of stator is installed to the stator and only allows rotary motion of the stator only in a circumferential direction.

16. dynaflow torque converter according to claim 1, wherein the inner ring limits the output hub of the torque-converters.

17. a kind of method for assembling dynaflow torque converter, method includes the following steps: providing can be around rotation axis The first shell shell and second shell shell of the shell of rotation；Pre-assembled torque-converters, the pre-assembled torque-converters are provided It include: impeller, the turbine and stator being axially oppositely disposed with impeller；Turbine includes turbine case and from the turbine case It extends radially inwardly and at least one holding plate with the turbine case one；There is provided allows the turbine only in a circumferential direction The unidirectional turbine clutch being rotated on direction, the unidirectional turbine clutch includes: outer ring；It is radially arranged in outer ring Interior inner ring；And the multiple joint elements being radially positioned between outer ring and inner ring, the multiple joint element are configured to permit Perhaps outer ring is only rotated in a circumferential direction relative to inner ring；Coaxially, no by the turbine and rotation axis It is rotatably connected to the outer ring of the unidirectional turbine clutch, so that at least one described holding plate setting of the turbine exists Between the stator and turbine one-way clutch；Torque-vibration damper is provided, the torque-vibration damper includes that can enclose The input link rotated around rotation axis, multiple elastic components circumferentially acted on, and be elastically attached to by elastic component The output link of the input link；The output link of the torque-vibration damper is non-rotatably attached to the whirlpool Wheel；And the input link of the torque-vibration damper is elastically mounted to by institute by the elastic component circumferentially acted on State the output link of torque-vibration damper.

18. according to the method for claim 17, further comprising the steps of: offer lock piston；And not by the lock piston It is rotatably attached to the input link of the torque-vibration damper.

19. according to the method for claim 18, wherein the input link of the torque-vibration damper passes through the circumferential direction The elastic component of effect is elastically mounted to the output link of the torque-vibration damper, enables the lock piston phase The inner ring of output link and the unidirectional turbine clutch for the torque-vibration damper moves axially.

20. according to the method for claim 17, wherein pre-assembled torque-converters includes turbine, and the turbine includes and institute State the substantially annular holding plate of turbine case one；And turbine is wherein non-rotatably connected to the unidirectional turbine The step of outer ring of clutch includes the outer ring that annular retaining plate is non-rotatably connected to the unidirectional turbine clutch Step.